Bundle tie feeder



y 1966 E. D. PIERSON ETAL 3,260,191

BUNDLE TIE FEEDER 9 Sheets-Sheet 1 Filed Oct. 8, 1964 INVENTORS EDWARD D. PIERSON WRIGHT JAM ES flan ATTOR NEYS y 2, 1966 E. D. PlERSON ETAL 3,260,191

BUNDLE T I E FEEDER 9 Sheets-Sheet 2 Filed 001;. 8, 1964 INVENTOR$ EDWARD D. PIERSON JAMES C. WRIGHT ATTORNEYS E. D. PIERSON ETAL 3,260,191

July 12, 1966 BUNDLE TIE FEEDER 9 Sheets-Sheet 5 Filed 001:. 8, 1964 SN m MOT SH N BER V W N S IDC v mafm mm W/ n E W6 A FIG.

y 2, 1966 E. D. PIERSON ETAL 3,260,191

BUNDLE TIE FEEDER 9 Sheets-Sheet 4 Filed Oct. 8, 1964 INVENTORS EDWARD D.P|ERSON JAMES C. WRIGHT FIG. 7

ATTORNEYS FIG. 8

y 1966 E. D. PIERSON ETAL 3,260,191

BUNDLE TIE FEEDER 9 Sheets-Sheet Filed Oct. 8, 1964 FIG. 10

FIG. 9

IBGAW y 1966 E. D. PIERSON ETAL BUNDLE TIE FEEDER Filed Oct. 8, 1964 9 Sheets-Sheet '7 EDWARD D. PIERSON JAMES C. WRIG T %'7 ATTORNEYS July 12, 1966 Filed Oct. 8, 1964 E. D. PIERSON ETAL BUNDLE TIE FEEDER 9 Sheets-Sheet 8 IlIlIlIlIlI I I I I V I SOL FIG. 2/

FIG. 20

INVENTORS EDWARD D. PIERSON JAMES WRIGHT July 12, 1966 Filed 001:. 8,

BUNDLE TIE FEEDER E. D. PIERSON ETAL 9 Sheets-Sheet 9 u 5542) un sezuv' L i afia) Q /55ec3) 564 see 560(3) .05 4-4 IBGCA) Z?- FIG. 22

IN EDWARD JAME VEN'TORS D. PIERSON C. WRIGHT ATTORNEYS United States Patent 3,260,191 BUNDLE TIE FEEDER Edward D. Pierson and James C. Wright, Denver, Colo., assignors to Miner Machine Company, Denver, Colo., a corporation of Colorado Filed Oct. 8, 1964, Ser. No. 402,534 19 Claims. (Cl. 100-4) This invention relates to a bundle tie feeder and, more specifically, to a device of the type aforementioned that automatically feeds stacks to the tyer, actuates the latter and subsquen-tly ejects the tied bundle.

There exist in the prior art many different bundle tying machines, the prime purpose of which is to fasten a loose stack of articles together into a unitary package by encircling same with a band of wire twisted at the ends. These wire tyers are used in many different industries to band such things as stacks of paper cartons, fruit boxes and newspapers. It is in the latter bundling problem that the present invention finds its prime utility.

These wire tie bundlers all involve some type of fiat horizontal support or table upon which the stack rests during the tying operation. They also usually have at least one upright Wall structure rising vertically above the table against which the side of the stack rests to hold same in fixed position while the tie is being effected. Ordinarily, the tyer is manually actuated by an opera-tor who depresses a foot pedal or some similar operating control. Wire tie machines employing these features are exemplified by US. Patents Nos. 1,933,473; 2,054,602; 2,054,603; 2,191,082; 2,206,299; and 2,206,300; all of which are suitable for use in bundling stacks of newspapers and are widely employed for this purpose.

Newspapers present a bothersome bundling problem because they slide around on one another, vary in thickness from edition to edition, and otherwise produce nonuniform stacks that are extremely difficult to handle. The usual result is that the stacks are fed to the tyer manually so that each can be given the attention it requires to place it in proper position for bundling. Wooden boxes, cartons and the like, on the other hand, can be handled automatically because of their rigidity and uniform shape.

It has now been found in accordance with the teaching of the instant invention that it is possible to eliminate handfeeding in favor of an automatic device that will introduce the stack, square it up on all four sides, hold it in place while being tied, operate the tyer and subsequently eject the tied bundle. Furthermore, these operations are all performed in the direct line of stack movement thus conserving plant space and eliminating the need for auxiliary apparatus to change the direction of stack progression or, more likely, an operator to manually transfer the stack from a conveyor line to the tyer and back again.

The unit herein described accepts a stack from an incoming conveyor line, senses its presence, delivers same to the tyer while simultaneously squaring it up, positions the stack to receive either a single or double tie, aotuates the tyer, senses completion Of the tying operation, and ejects the finished bundle. In the case of a double tie, the feeder automatically stops the stack in position to receive the first tie, actuates the tyer, senses completion of the first tie, moves the bundle forward into position for the second tie, again aetuates the tyer, and finally eject-s the bundle. Means are also provided for shifting the feeder instantly between single and double tie operation. Furthermore, the feeder can be placed in manual-mode so that an operator can handle unusual tying problems such as, for example, multiple tie-d bundles, different goods and special shapes.

The ejection mechanism is unique in that it will retract 3,260,191 Patented July 12, 1966 and allow a stack to pass over it before moving forward into position for ejection. This feature eliminates any delay in ejection and otherwise speeds up the entire tying operation. A stack-pusher or follolwer mechanism provided on the feeder engages the adjacent rear corner of the stack and introduces same onto the tyer table against the upright fixed stop usually provided thereon. A portion of the feeder also engages the leading face of the stack and stops it in correct position for the tie to be applied thereto. This movable stop mechanism can be preset to position the stack for either single or double-tie operations. The stack-pusher mechanism and movable stop cooperate with one another to correctly locate the bundle for either mode of operation and, in the case of the double-tie function, move the stack in two increments before triggering the ejector.

A stack-detector switch on the conveyor table of the feeder senses the presence of an incoming stack and readies all functional elements of the feeder for subsequent operation. This same switch releases to initiate the entire cycle of operations performed by the feeder.

It is, therefore, the principal object of the present invention to provide a novel and improved feeder for bundle tying machines.

A second objective is the provision of a device of the type aforementioned that accomplishes the stack'lfeedin tyer-actuating and bundle-ejecting functions entirely automatioally. Another object of the invention is to provide a control mechanism for a wire-tie bundle-r that will automatically program and actuate same for either single or double tie operation.

Still another objective of the invention herein described and claimed is the provision of a wire tyer feeder specifically designed for in-line operation.

An additional object is to provide a feeder apparatus that cooperates with the tyer to square all four upright faces of a rectangular stack. of loosely-layered articles preparatory to tying same into a unitary bundle.

Further objectives of the invention are the provision of a bundle-tyer-feeder that is rugged, fast, easy to use, adaptable with a minimum of modification to various types of tying machines, compact, versatile and even decorative in appearance.

Other objects will be in part apparent and in part pointed out specifically hereinafter in connection with the description of the drawings that follows, and in which:

FIGURE 1 is a top plan view of the feeder unit of the present invention with portions of the roller conveyor assembly broken away to reveal the drive therefor and with the stack pusher or follower mechanism shown in diametrical section;

FIGURE 2 is a fragmentary vertical section slightly enlarged taken along line 22 of FIGURE 1, portions having been broken away and shown in section to better show the internal workings;

FIGURE 3 is a vertical section taken along line 3-3 of FIGURE 2 which, once again, has portions broken away and shown in section;

FIGURE 4 is a fragmentary section taken along line 44 of FIGURE 3 detailing the drive for the overhanging roller conveyor section;

FIGURE 5 is a fragmentary section taken along line 5-5 of FIGURE 4 showing how the belt is reeved across the top of the roller making up the overhanging roller conveyor section;

FIGURE 6 is an enlarged fragmentary detail of the stack-detector switch;

FIGURE 7 is a section taken along line 77 of FIG- URE 6;

FIGURE 8 is a fragmentary detail of the mechanism operative to actuate the foot switch of the tyer;

FIGURE 9 is an enlarged fragmentary section taken along line 9-9 of FIGURE 1 showing details of the stack-pusher or follower mechanism;

FIGURE 10 is a fragmentary detail of the cam and microswitches operated thereby that control the several functions of the feeder during the feed and return cycles;

FIGURE 11 is a further enlarged end view of the FIG- URE 10 mechanism showing the track along which the switch elements can be adjusted;

FIGURE 12 is a somewhat diagrammatic top plan view of the feeder showing the stack positioned on the tyer table in position to be tied;

FIGURE 13 is a fragmentary section taken along line 1313 of FIGURE 1 showing the details of the ejector mechanism;

FIGURE 14 is a fragmentary top plan view of the retractable hinged ejector plate;

FIGURE 15 is -a section taken along line 1515 of FIGURE 13;

FIGURE 16 is a fragmentary section slightly enlarged taken along line 1616 of FIGURE 15;

FIGURE 17 is an enlarged fragmentary detail, portions of which have been broken away and shown in section, illustrating the retractable stop assembly;

FIGURE 18 is an elevational view of the mechanism of FIGURE 17 to the same scale, portions of which have been broken away and shown in section;

FIGURE 19 is a fragmentary detail showing the microswitch and cam-actuator therefor mounted on the single revolution shaft of the tyer;

FIGURE 20 is a schematic diagram showing the hydraulic system that controls the movements of the follower assembly;

FIGURE 21 is a schematic diagram of the pneumatic assembly that controls the follower flap, squaring flap, retractable stop mechanism, tyer interlock and ejector mechanism; and,

FIGURE 22 is a schematic wiring diagram illustrating the electrical circuitry that controls the various functional assemblies of the feeder.

Before proceeding with the detailed description of the drawings, it is advisable to explain briefly how the feeder of the present invention integrates with the various different types and styles of bundle tyres even though these same matters will be set forth more explicitly as the ex- 'planation of the various elements proceeds. Common to all bundle tyers is a flat horizontal support that holds the stack while the tie is affixed thereto. The bundle follower or pusher of the feeder cooperates with the bundle stop to square up the stack and properly position same on the tyer table. In some instances it might be necessary to alter the dimensions of the tyer table to accommodate the above-described elements of the feeder, but, little else would likely be required.

Most tyer units have at least one upright abutment positioned to engage the side of the stack nearest the operator and, if so, the follower of the feeder will push the stack against this abutment and the stop on the feeder that engages the lead face of the stack. In any event, the retractable stop mechanism of the feeder carries a fixed abutment that serves this important function.

Common to all tyers is, of course, some actuating means for initiating the tying operation. This customarily takes the form of a foot pedal that is depressed by the operator, hence, the feeder herein described is shown equipped with a foot-pedal actuator. Obviously, should the tyer have some other type of actuating mechanism, the feeder can easily be modified by one having ordinary skill in the mechanic-a1 arts to operate such other mech anism.

The only other requirement is the location of means on the tyer which can be used to signal the completion of the tying cycle so that the feeder can initiate the ejection operation. There are several elements on any tyer that cycle in synchronization with the tying cycle and can, therefore, be used to signal the completion thereof. As illustrated herein, one of the shafts of the tyer that makes a single complete revolution in synchronization with the tying cycle is equipped with a cam that trips the ejection mechanism of the feeder upon completion of the tie. There are, of course, many other ways this can be accomplished, all of which are well within the skill of an ordinary mechanic and the one illustrated merely exemplifies one such approach to the problem.

Proceeding now with a detailed description of the invention and, initially, to FIGURES 1, 2 and 3 for this purpose it will be seen that the feeder has the various functional elements thereof contained within a base that has been indicated in a general way by reference numeral 10 and will be seen to include front and rear sidewalls 12 and 14, respectively, right and left endwalls 16 and 18 as viewed from the position of an operator standing in the left margin looking at FIGURE 3, a bottom 20 supported above ground level by adjustable legs 22 at the corners, and a roller conveyor top that has been broadly referred to by numeral 24. In the particular form shown, the base 10 is more or less box-like and houses in its interior the motor 26, pump 28, pneumatic cylinder 30, the belt drives 32 for the roller top together with the various linkages and piping that operate the follower assembly which has been broadly designated by numeral 34 and the ejector mechanism similarly referred to by numeral 36.

The roller conveyor subassembly 24 is the first of the several subassemblies that requires detailed analysis and, for this purpose, reference will be made to FIGURES 16, inclusive, and 12, all of which show various elements thereof. Gear motor 26 having a double-ended output shaft 38 is mounted inside the base 10 adjacent left endwall 18 on bracket 40 secured to the bottom wall 20. The motor is centrally located with the shaft extending transversely on both sides thereof. Two V-belt pulley 42 are mounted on each projecting end of the motor shaft in spaced relation to one another.

Extending lengthwise of the base between the endwalls 16 and 18 are a pair of spaced substantially parallel frame elements 44 through which are mounted a plurality of longitudinally-spaced parallel pulley shafts 46, on opposite ends of which are journalled pulleys 48. Pulley pairs 48 are coplanar with pulley pairs 42 as shown in FIG- URE 3 so as to receive V-belts 50 which are reeved thereover in a manner to be explained presently. Still other pairs of pulleys 52 are mounted on shafts 54 that pass through brackets 56 attached to the underside of frame elements 44. The latter pairs of pulleys maintain the V- belts 50 tarut, the latter passing under pulleys 42, then along the top of pulleys 48, back and over pulleys 52, and finally, returning to pulleys 42 as shown most clearly in FIGURE 2.

Resting'upon the portion of the V-belts 50 that run along the top of pulleys 48 are a pair of roller conveyor sections 58F and 58R. Each section has inner and outer sideframe elements 60 and 62 lying in spaced parallel relation to one another and spanned by a plurality of rollers 64 journalled therebetween. The ends of the outer frame elements 62 that terminate adjacent the endwalls 16 and 18 have downturned portions 66 that fit into the notches 68 provided in brackets 70 secured to said walls thus retaining the roller sections against lateral movement. Each roller rests on two belts as can be seen in FIGURES 1 and 4 which drive same in a direction to move a stack of newspapers or other articles to be bundled onto the tyer.

One of the forwardmost pulley shafts 46M is slightly longer than its counterpart and is fitted with a sprocket 72 that is most clearly revealed in FIGURE 4. Bearings 74 of the inside of right endwall 16 journal shaft 76 that carries a second sprocket 78 along with a pair of flat belt pulleys 80. An L-shaped bracket 82 and stub shaft 84 journal a third idler sprocket 86 in vertical alignment with sprockets 72 and 78. Sprocket chain 88 is reeved over sprocket 72 across drive sprocket 78 and around idler 86 thus driving shaft 76 in the same direction as the pulley shafts 46 from gear motor 26.

Few of the commonly used tyers include conveyors built into their tying tables, but instead, have a sunken or otherwise recessed portion adjacent the inlet edge there of adapted to accommodate the end of an ordinary conveyor used to deliver the stacks to the tyer. Without a conveyor to move the stacks part way across the tyer table, they would stop short of the position required for the tying operation and necessitate an operator to feed them to the machine. A conveyor, on the other hand, overlying the tyer table can be used to move the stacks to a position only a few inches short of that Where the tie is made, the remaining distance being taken care of in accordance with the present invention by follower assembly 34 soon to be described.

Therefore, because a portion of the roller conveyor mechanism 24 will usually overlie the tyer table 90 (dotted lines in FIGURE 1) it has been shown made in two sections; the first, the :underdriven sections 58F and 58R, already described; and the second, the overhanging sections 94F and 94R. Sections 58, of course, have the pulleys, drive shafts, motor and associated elements lying directly beneath the rollers and cannot, therefore, project over onto the tyer table. overhanging sections 94, on the other hand, are so designed and constructed that they are substantially. unobstructed underneath and can project over onto the tyer table.

Rollers 64 are, as before, secured for rotation in sideby-side parallel relation within a frame that has been broadly designated by numeral 96. The manner in which frame 96 of the overhanging conveyor section is connected to the main feeder frame can best be seen in FIGURES 13, and 16 to which reference will now be made. The upstanding siderails 98 of frame 96 are welded or otherwise secured to a bedplate 100 that has a pair of pins 102 projecting upwardly at the transverse centerline thereof between the rails. As already noted, both the underdriven conveyor sections 58 and the overhanging sections 94 are further subdivided into front and rear sections 58F, 58R, 94F and 94R that are separated by a longitudinally extending ejector track 104 that lies flush with the upper roller surfaces and also projects to the right of the base beyond right endwall 16 (FIGURE 13). A block having a channel 108 in the upper surface thereof sized to receive the projecting end of the ejector track is secured to the underside of the latter and, in turn, contains openings 108 in its bottom surface located to accept the pins 102 of the frame bedplate 100. As shown in FIGURE 13, the roller frame bedplate is slipped up under block 106 with the pins 102 seated in their holes 108 and then the bedplate is moved over the top of the tyer table 90, the latter actually supporting same. In certain popular wire tyers as previously mentioned, a recess is provided in the tyer table and bedplate 100 is sized to fit this recess thus forming a mechanical interlock between the feeder and tyer maintaining them in correct relation to one another. As shown in FIGURE 2, the rollers 64 are mounted in the overhanging frame such that they produce a slight downward inclination toward the right or tyer entry.

FIGURES 2, 4 and 5 reveal the drive for the overhanging conveyor sections 94R and 94F which will be seen to comprise flat endless belts 110 that pass around pulleys 80, across the top of all but the endmost roller 63 which acts as an idler roller, back along the bottom of the rollers and over idler roller 112 (FIGURE 5). Portions of the newspaper stacks are, therefore, conveyed on both the roller surfaces and the exposed belt surfaces as they pass along the overhanging conveyor sections 94.

Before proceeding with the description of the stackpusher assembly 34 it would, perhaps, be well to explain the actuating mechanism that has been broadly designated by reference numeral 114 and which is clearly displayed in FIGURES 2, 6 and 7. Two of the rollers 64M (FIG- URE 6) adjacent the discharge end of the underdriven conveyor section 58F are foreshortened to accommodate trigger 116 which is rockably mounted on one of the ,roller shafts 118. An adjustable stop 120 is attached to the roller frame in position to engage the underside of the trigger and limit the extent to which it may be depressed. A suitable bracket 122 is also attached to the roller frame in position to support switch 124 that is depressed by the trigger to initiate the tying cycle in a manner to be explained presently.

Trigger 116 projects upward slightly above the plane of the conveyor rollers so that a stack of newspapers passing across the feeder will engage same. The leading edge 126 of the trigger is inclined upwardly and toward the right from a point beneath the conveyor surface so as to present no corner that would catch the bottom paper of an incoming stack. As the stack passes beyond trigger 116, it pops back up under the influence of switch 124.

Next, reference will be made to the figures of the drawing that shows the stack-pusher assembly 34, namely, FIGURES 1, 2, 3 and 9-12 inclusive. As seen in FIG- URE 3, the legs 22 of the base are adjustably fastened into nuts 128 that are welded to L-brackets 130 and the latter are, in turn, welded to the underside of hollow rectangular horizontal frame members 132 that run along the bottom of the base 10 at the front and rear thereof. The bottom wall 20 rests on these frame members with the front and rear walls 12 and 14 extending upwardly therefrom. Similar hollow rectangular uprights 134 rest on the bottom and support the upper hollow rectangular horizontal frame elements 136.

The front wall 12 has an inturned flange 138 along its upper edge that terminates at the near side of the adjacent roller conveyor sections 58F and 94F; whereas, the rear edge of the feeder is provided with a pre-cast metal bracket 140 that is fastened directly to the rear upper horizontal frame element 136 and functions as a support for the entire stack-pusher assembly. This bracket has a horizontal flange 142 attached to frame element 136, an upstanding wall including a vertical section 144 topped by an upwardly and forwardly inclined portion 146, the terminal edge of which is outturned to define flange 148 having a downwardly-opening groove 150 therein. The bracket projects well beyond the right and left endwalls of the base, is open on the right end and has an outturned flange 152 on the left end to which is secured one end of hydraulic cylinder 154. Fastened to vertical wall portion 144 of bracket 140 is a horizontal rail 156 which, in the particular form shown, has a generally key-hole shaped cross-section and which parallels the hydraulic cylinder directly therebeneath. Mounted on rail 156 for horizontal sliding movement along the rear edge of the feeder is a pusher-support bracket or hydraulic ram 158 that includes a pair of horizontally-spaced bosses 160 that have key-hole-shaped slots 162 therein adapted to receive the correspondingly shaped rail 156. Ram 158 also includes a Web 164 to which is fastened the piston rod 166 of the hydraulic servo-motor. Proper alignment of the hydraulic ram and the elements associated therewith is maintained by trunnions 168 mounted atop said ram in position to ride along in the groove 150 in the underside of flange 148.

Mounted on top of flange 148 of main support bracket 140 is a switch track 170. As can best be seen in FIG- URES 10 and 11, this track has an upwardly-opening generally T-shaped groove 172 therein defined by inturned flanges 174. Slidable along the top of the switch track are a plurality of L-shaped switch-mounting brackets 176 which are releasably fastened thereto by bolts 178 passing through the horizontal flange 180 thereof and into pressure plate 182 that is lifted into engagement with the undersides of flanges 174.

Attached to the vertical flanges 184 of the L-brackets are microswitches 186 of the type having roller actuators 188 projecting forwardly into the path of switch-operator 190 (FIGURE 10) that is carried atop hydraulic ram 158 for movement therewith. The switch operator is of the cam-type having oppositely-inclined faces 192 and 194 adapted to actuate the switches on both the forward and return strokes of the pusher assembly. The several switches can, therefore, be adjusted along the track so as to energize various elements of the feeder unit at the desired intervals during the feeding, tying and ejecting operations. A cover plate 196 attached to the main bracket 148 forms a roof over the switches and protects same against foreign matter which can easily foul the contacts or otherwise cause a malfunction.

Attention is now directed to FIGURES 1, 2, 9 and 12 wherein is shown the flap assembly that swings out against the adjacent corner of the stack and squares it up while simultaneously pushing it forward into the dotted line position of FIGURE 12 where the tie is applied. In FIGURE 9 is will be noted that rail-mounted hydraulic ram 158 has, at the forward end thereof, a continuation of web 164 extending toward the front of the feeder and which includes along its forwardmost edge a verticallyoriented bearing 198 adapted to journal shaft 208 for rotational movement therein. A sizeable notch 202 is provided in this portion of web 164 positioned to separate the bearing into upper and lower sections with the shaft exposed therebetween. Mounted on the exposed portion of the shaft is a segment of a pinion 204 which is fastened thereto by pin 206 and with the teeth 208 facing into the notch. Collars 210 above and below the pinion separate same from the adjacent faces of the shaft bearings.

Shaft 220 projects well above and below its bearings and the follower flap 212 is provided with integrallyformed arms 214 that terminate in sleeves 216 which fasten to said shaft by means of pins 218 both above and below the bearings 198. Thus, rotation of shaft 280 by means of pinion 204 will cause the follower flap 212 to swing to-and-fro in a vertical plane.

A squaring-flap 1220 having arms 222 terminating in sleeves 224 is likewise, mounted on the ends of shaft 201) that project above and below the sleeves of the follower flap, however, the squaring flap is not fastened to the shaft, but rather, mounted for pivotal movement relative thereto with collars 210 separating same from the corresponding parts of the follower flap.

Now, as seen in FIGURE 1, ram 158 has a forwardlyprojecting web 226 at its left extremity which parallels web 164 and provides an abutment for attachment of pneumatic servo-motor 228. The axis of this servomotor is aligned with notch 202 in web 164 and its piston rod 230 carries a rack 232 that meshes with the pinion 204. Web 226 also carries a deflector plate 234 (FIG- URE 1) positioned and shaped to guide a stack moving across the conveyor table around ram 158. The portion of notch 282 within which rack 232 reciprocates is preferably bordered by a guide-piece 236 which provides a track therefor.

A clevis 238 is provided on the right side of web 164 which pivotably mounts another pneumatic servo-motor 240 that has its piston rod 242 attached pivotally to the rear face of squaring flap 220 as shown in FIGURE 1. By referring to FIGURE 1 it will be seen that upon actuation of servo-motor 228 so as to extend its piston rod v230, rack 232 will turn pinion 204 clockwise and cause the follower flap to swing back into folded position alongside an incoming stack (full-line position of FIGURE 12). Conversely, actuation of servo-motor 228 in a direction to retract its piston will swing the follower flap out into position behind the bundle where it will function to push same onto the tyer table as the ram 158 is pushed to the right along its track 156 by hydraulic servomotor 154. Similarly, actuation of servo-motor 240 in a direction to extend its piston rod 242 will extend squaring flap 220 from its folded full-line position shown in FIGURE 12 to the dotted-line extended position of this same figure where it will engage the rear face of the stack and square it up against the upright guides 244 and 246 provided for this purpose on the tyer table. In folded or retracted position the squaring flap 220, of course, permits the incoming stacks to move freely past onto the table overhanging section 94 of the roller conveyor.

Briefly referring to FIGURES 2 and 3, the hydraulic fluid for operating hydraulic motor 154 is stored in a shallow sump 248 suspended between frame elements 132 of the base underneath bottom wall 20. Pump 250 draws fluid from the sump through tube 252 and into a hydraulic control valve 256 (FIGURE 20) that controls servo-motor 154. This valve 256 is, in turn, actuated by certain of the switches 186 in a manner to be described presently. Hydraulic lines 258 and 260 connect into opposite ends of the hydraulic servo-motor.

Pneumatic servo motors 228 and 240 are powered by an in-plant source of compressed air (not shown) which also powers the mechanical interlock between the feeder and tyer, the retractable stop mechanism and the ejector mechanism, all of which will soon be described in detail. The first of these pneumatic systems to be set forth in detail is the interlock between the. tyer and feeder that has been shown in FIGURE 8 and broadly designated by reference numeral 262. A suitable solenoid valve 264 adapted to be opened as the switch actuator passes one of the switch contacts 188 of the stack-pusher mechanism admits compressed air to a quick-exhaust valve 266 by means of conduit 268 and from there into pneumatic servo-motor 270 which trips the tyer foot switch 272. A bracket 274 fastens the above-described assembly to the tyer. Servo-motor 270 will, of course, vary in design and operation depending upon the type of control the tyer carries for actuating it. In the FIGURE 8 embodiment the servo-motor is of a type specifically adapted to operate a foot pedal or similar element.

Now, in most of these tying machines the tripping mechanism, whether it be a pedal or otherwise, must be held in actuated position until just before the machine finishes the tie. The feeder, on the other hand, must also receive notification from the tyer that the tie is complete so that the feeder can begin the ejection of the finished bundle. One of the common newspaper bundle tyers includes a shaft that makes a single full revolution during each tying cycle and it is a simple matter to apply a trip cam to this shaft and add a micro-switch that will be actuated thereby to begin the ejection cycle of the feeder. Such an arrangement has been illustrated in FIGURE 19 where the single-revolution tyer shaft has been given reference numeral 276 and has been shown equipped with a single-lobed cam 278 that rotates therewith. Shaft 276 is analogous to shaft 57 of U.S. Patent 2,206,299 which is described in column 11 beginning at line 73 and continuing into column 7 down through line 3. It will be noted that this shaft is, likewise, a single revolution shaft and that the tyer stops signalling completion of the tie as soon as the single turn is completed. There are, of course, many shafts, gears and other elements in a bundle tying machine which rotate a specific number of turns or fraction thereof during the tying cycle and could be used for the same purpose. As the shaft and cam associated therewith turn counterclockwise as shown in FIGURE 19, the cam trips switch 280 mounted on bracket 282 thus signalling completion of the tie and energizing the ejector mechanism 36 of the feeder in a manner soon to be described. Switch 280 does not, however, close valve 264 as this has been accomplished by a clock timer just prior to the completion of the tie. The reason for this is that most tyers require that the foot pedal or other actuator be depressed and held down for a certain minimum time interval before the tyer will run through its full tying cycle; yet, if this .actuator is held down until the tie is complete it will oftentimes begin a second tie. Therefore, at the same time the tyer is actuated and servo-motor 270 is energized, a clock-timer is started which holds valve 264 open for the predetermined time interval required to insure the tyer will complete the tie. Once this interval has elapsed, the timer allows valve 264 to close and also instantly opens exhaust valve 266 to effect an immediate release of the foot pedal. This all occurs, however, before switch 280 has actuated to signal completion of the tie. It is, of course, quite possible that other tyers could utilize the signal from switch 280 to open valve 264 thus eliminating the clock-timer altogether.

The next element of the pneumatic system requiring detailed analysis is the multi-position bundle-stop assembly shown in FIGURES 12, 17 and 18 to which reference will now be made. As previously mentioned, table 90 forms a part of the tyer and usually includes the upright stop 244 although, if it does not, it can easily be added. The squaring flap 220 pushes the stack up against this stationary abutment 244 and thus squaring up the front and rear faces thereof. The retractable stop assembly that has been broadly referred to by reference numeral 284, on the other hand, cooperates with the follower flap 212 to locate the stack for the tie and also square the right and left faces thereof. This retractable stop assembly is mounted atop the tyer table by means of support frame 286 that has slotted ears 288 which provide for limited transverse adjustment. Stationary abutment 246 forms a part of the retractable stop assembly and is secured to the support frame by means of a slotted connection 290 that permits said stop to be aligned with the tyer stop 244.

A vertical pivot 292 is mounted adjacent the rear edge of the support frame and a tubular element 294 having vertically-shaped parallel crank arms 296 projecting therefrom is mounted for pivotal movement on said pivot. These crank arms are generally L-shaped and carry a pin 298 upon which is mounted three rollers 300, one located between the arms, a second above the upper one and the third below the lower arm. Intermediate the ends of the lower arm is an car 302 that is pivotally attached to clevis 304 (FIGURE 17) carried on the end of piston rod 306 of main pneumatic servo-motor 308. This servo-motor is, in turn, pivotally attached to one end of rocker link 310 which is pivotally mounted on pivot 312 at a point intermediate its ends. Pivot 312 projects vertically from the support frame 286 adjacent the front edge thereof and, as aforesaid, mounts rocker link 310. The other end of this rocker link is slotted at 314 to receive fastener 316 that adjustably interconnects the rocker link with adjusting link 318. Adjusting link 318 is, in turn, pivotally attached to clevis 320 on the piston rod 322 of double-tie pneumatic servo-motor 324. This servo-motor is pivotally mounted on the frame at 326.

Also carried by the support frame are a main servomotor control valve 328 and double-tie servo-motor control valve 33ft, both of which are connected to the plant air supply. Conduits 3-32 and 334 connect valve 328 into opposite ends of the servo-motor 308; whereas, conduits 336 and 338 operatively connect valve 330 into servomotor 324.

The feeder has a function selector switch which programs the retractable stop 284 for automatic single-tie operation, automatic double-tie operation or manual operation, the stop being retracted and inoperative in manual-mode. Irrespective of the mode of operation selected, the tyer operates the same way but the retract able stop and follower assemblies function differently.

The simplest operation is, of course, the manual mode where the entire feeder is inoperative except for the conveyor and part of the ejector. The stacks are positioned by hand, the tyer tripped manually and the finished bundle ejected by hand.

Next is the single-tie mode wherein only valve 328 is actuated to operate the main pneumatic servo-motor 308 and swing arms 296 from the full-line position of FIG- URE 17 into the dotted-line position A. With the rollers 300 of the retractable stop in position A, the stack is located so that the tie will be made at approximately the, center of the bundle. Then, upon completion of the tie, the finished bundle is ejected from the tyer by ejector mechanism 36. Thus, in single-tie mode, control valve 330 and double-tie servo-motor 324 are completely inoperative. In fact, pneumatic motor 308 functions as if pivot 3-40 were stationary.

When in single-tie mode, a stack passing over and off of trigger 114 immediately starts the follower mechanism to the right as viewed in FIGURE 2 and, simultaneously, energizes pneumatic servo-motors 228, 240 and 308 to extend the follower flap, the squaring flap and to move the retractable stop into single-tie position A of FIG- URE 17. Thus, by the time the follower reaches switch 1860, the stack is squared up on all four sides ready for the tie to be applied thereto. Switch 186C, therefore, initiates retraction of the follower mechanism 34 as well as retractable stop mechanism 284, the latter moving out from ahead of the stack while the tie is being applied thereto. As will be explained presently in connection with the pneumatic diagram (FIGURE 21) air is bled from behind the piston of servo-motor 308 at a controlled rate so that the movable stop actuated thereby retracts rather slowly while the tie is being applied to the stack.

The double-tie mode is slightly more complex than the single-tie mode. Setting of the mode switch (FIGURE 22) in double-tie mode sets the circuit to open valve 330 and extend the piston rod 322 of pneumatic servomotor 324 simultaneously with servo-motor 308. Thus, as the stack moves off of trigger 114, servo-motors 308 and 324 are actuated simultaneously moving the rollers 300 all the way over to position B. This, of course, stops the stack short so the tie will be applied nearer its right end than the left. Switch 18613 is now in circuit and it operates to shorten the initial stroke of the follower mechansm so that corresponding to position B of the retractable stop. In this instance the follower does not retract to its starting position as soon as the stack is in position for the first tie, but rather, stays put until it receives a signal from switch 280 that the first tie is complete, whereupon, it moves forward again pushing the once-tied stack ahead of it past switch 186C until it reaches switch 186D. The retractable stop 284 has, in the meantime, started to retract just as in the single-tie mode commencing when the stack is in correct position for the first tie. The exhaust from servo-motor 338 is controlled such that the rollers 300 have reached approximately position C on their path to retracted position at the time the first tie is completed and the follower begins, once again, to push the bundle. Thus, the follower is pushing the once-tied bundle against stop 284 while it is still moving slowly out of the way. When the follower reaches switch 186D that is now in the circuit, it stops, leaving the bundle in position for the second tie made nearer its left end. Actuation of switch 186D initiates the tyer a second time and also retracts the follower while folding the follower flap and squaring flap. Upon completion of the second tie, the follower is already retracted as is the movable stop 284 which has continued to retract all the time the second tie was being applied. Completion of the second tie again actuates switch 280 but this time it starts the ejector as in the single-tie mode.

'Of the several mechanical elements in the system, there remains to be described ejector mechanism 36and, for thus purpose, reference will be made to FIGURES 1, 2, 3, 4 and 12-15, inclusive. Extending the full length of the feeder top between the front and rear roller conveyor sections is a hollow rectangular frame element 342 attached to the right and left endwalls by brackets 1 1 344. Elongate slats 346 and 348 are provided in the top and bottom, respectively, of this frame clement adapted to receive the crank arm 350 and mounting bracket 352 of the ejector slide 354.

Bottom wall 20 of the base has a pair of upstanding brackets 356 mounted thereon (FIGURE 3) with a pivot pin 358 extending therebetween. Mounted on this pivot pin for rotational movement is sleeve 360 with bushings 362 at opposite ends thereof. Crank arm 350 is welded or otherwise attached to one end of sleeve 362 so as to extend upwardly and to the left (FIGURE 13) in a vertical plane centered between the front and rear walls 12 and 14. The other end of sleeve 360 is provided with a second crank arm 364 whose free upper end is pivotally attached to clevis 366 of pneumatic servo-motor 30. This servo-motor is, in turn, pivotally attached to left end wall 18 by clevis 368.

As seen in FIGURE 13, the ejector slide 354 has bracket 352 mounted on the underside thereof near its left extremity and a link 370 with bifurcated end portions pivotally interconnects the bracket 352 and the upper end of crank arm 350 within the confines of element 342. The crank arm operates within slot 348 while bracket 352 moves within slot 346.

Pneumatic servo-motor 30 is operated by the plant air supply and its movements are controlled by two separate solenoid valves which will be described in detail in connection with the pneumatic diagram (FIGURE 21). Piston rod 372 of the pneumatic servo-motor 30 is biased into partially extended position by a compression spring 374 that abuts the cylinder head and clevis 376.

Slide 354 is mounted for longitudinal slidable movement within the T-shaped track 376 in the underside of element 104. Examination of FIGURE 13 will reveal that actuation of pneumatic cylinder 30 in a direction to extend piston 372 will swing both crank arms 364 and 350 to the right thus acting through link 370 and bracket 352 to extend ejector slide 354 into the position shown in FIGURE 16. As shown in FIGURES 13 and 16, element 204 terminates short of the right end of element 106 and a cover plate 378 is attached to the latter in flush relation to the top surface of the track.

The right extremity of slide 354 is provided with a retractable flipper 380 which folds into horizontal position under cover plate 378 out of the way of an incoming stack upon full retraction of the ejector mechanism which is brought about by admitting air through one of the control valves into the head end of servo-motor 30 thus retracting the piston rod and compressing spring 374. As soon as an incoming stack passes over trigger 114, however, the valve holding the ejector fully retracted is de energized permitting spring 374 to partially extend the ejector an amount which will allow flipper to pop up into vertical position behind the stack that has just passed over the trigger. The second valve controlling full extension of the ejector will not operate, however, until the bundle is tied.

Flipper 380 is formed in'two sections 382 and 384 that interlock on pin 386 to form a hinge. Section 384 is fastened in fixed position to the right end of the slide while the other section 382 is normally biased into upright operative position by spring 388. As the slide retracts immediately following ejection of a finished bundle, the flipper 380 will strike corner plate 378 and fold down. De-energization of the relay which controls the valve that holds the ejector fully retracted allows the piston to float and spring 372 will partially extend the ejector from under cover plate 378 permitting the flipper to pop up behind the stack ready to eject same.

The first of the control circuits requiring detailed analysis is the hydraulic system that extends and retracts the follower or stack-pusher assembly 34 that has been illustrated in FIGURE 20. A four-way solenoid valve 390 is connected between the sump 248 and the hydraulic servomotor 154. Pump 250 draws fluid through line 252 continuously and normally returns same to the sump through by-pass 392 in the valve and the return line 394. Release of trigger 114 in response to a stack leaving same actuates solenoid 396 cutting off the by-pass 392 and delivering fluid through passage 398 and conduit 258 to the left side of servo-motor 154 causing it to actuate into extended position or feed the stack to the tyer. At the same time, of course, fluid is being exhausted ahead of the piston and returned to the sump through line 260, passage 400 of valve 390 and return line 394. Conversely, when the follower slide reaches switch 186C in a single-tie mode, solenoid 402 of valve 390 is actuated to reverse the flow of fluid to the piston by using passage 404 to interconnect feed line 406 with conduit 260 while the other passage 408 is connecting line 258 and exhaust line 394. When the slide reaches switch 186A, solenoid 402 is dc-energized. Solenoid 396 is de-energized as soon as 402 is energized.

The operation of the forward solenoid 396 and return solenoid 402 of hydraulic valve 390 are the same as described above for the double-tie mode except that they are actuated at different times and for different intervals. In the interests of clarity, however, the detailed description of the double-tie mode along with more complete details on the single-tie mode will be deferred until the electrical circuitry is explained in connection with FIG- URE 22.

Next, the pneumatic system illustrated schematically in FIGURE 21 will be set forth. Main air supply line 410 is connected into manifold 412 from which branch feed line 414 is connected into flap control valve 416 which is normally biased by spring 418 into the position shown where the supply air is fed through valve passage 420 and line 422 that branches to simultaneously pressurize the rear end of follower flap cylinder 228 by means of branch 424 and the front of squaring flap cylinder 240 through branch 426. The front of follower flap cylinder 228 and the rear of squaring flap cylinder 240 are similarly interconnected by lines 428 and 430 into common line 432 that leads through another passage 434 in valve 416. Passage 434 is open to the atmosphere thus exhausting air from the front of cylinder 228 and the rear of cylinder 240. As already explained in connection with FIGURES 1 and 2, the above-described positions of pneumatic servomotors 228 and 240 hold both the follower flap and squaring flap in retracted or folded position. Now, as soon as a stack leaves trigger 114, solenoid 436 of valve 416 is actuated against the bias of spring 418 to connect the supply line 414 into line 432 through valve passage 438 while passage 440 is exhausting air from cylinders 228 and 240 through line 422. This, of course, extends both flaps 212 and 220 into their extended or operative positions where they engage the left rear corner of the stack.

In both the single and double-tie modes, solenoid 436 actuating flap control valve 416 is de-ene-rgized by the same signal that energizes the follower return solenoid 402 of hydraulic valve 390 as will be seen presently.

Before proceeding with a description of the pneumatic hook-up to the tyer interlock it would be well to explain the function of the several valves 442 that appear at various points in the pneumatic system. These valves merely meter the flow by controlling the exhaust air. Each includes a ball check 444 that allows relatively unrestricted flow of high pressure air from the supply into the several pneumatic servo-motors 228, 240, 30 and 324. When, however, the line containing valve 442 serves as an exhaust line, ball check 444 closes and redirects the exhaust air past adjustable bleed orifice 446 thereby controlling the speed of the servo-motor.

Branch 448 from supply manifold 412 is connected into tyer trip solenoid valve 264 which is normally biased by spring 450 into the position shown where the plant air supply is cut off from tyer tripcylinder 220. Passage 452 of the valve 264'is open to the atmosphere bleeding line 268 connected into exhaust valve 266. This passage 452 could, of course, be connected directly into the rear end 113 of the tyer trip cylinder 220 eliminating valve'266 altogether and be used to exhaust air from behind the piston 454 which is normally biased into retracted position by spring 456. To do so, however, would necessitate the use of a rather large and expensive solenoid valve 264 as it is necessary to release the tyer trip cylinder rather quickly 1 or it will hold down the tyer foot pedal long enough to initiate a second unwanted tie. Therefore, in the particular embodiment shown, quick exhaust valve 266 is shown connected between the solenoid valve and the tyer trip cylinder. This valve is normally biased into exhaust position by spring 458 which opens the rear end of the tyer trip cylinder to the atmosphere through exhaust passage 460 as shown. Now, when solenoid 462 of valve 264 is tripped to connect the supply air through passage 464 and 268 into the exhaust valve 266, a diaphragm 465 shifts valve 266 to the left against the action of the spring 458 and connects the main supply air into the tyer trip cylinder through passage 466. This immediately extends the piston rod 468 of the tyer trip actuating the foot pedal of the tyer for the pre-determined interval set into clock timer 470 (FIGURE 22). As soon as the clock timer deenergizes solenoid 462 cutting off the supply air to the diaphragm 465 of valve 266, spring 458 shifts same into exhaust position instantly emptying cylinder 220.

Next to be considered in the pneumatic system is the retractable bundle stop mechanism 284. Branch air line 472 from the air manifold divides into lines 474 and 476 to feed air to solenoid valves 328 and 330 that control the movements of pneumatic servo-motors 308 and 324, respectively.

As previously mentioned, pneumatic servo-motor 324 is completely inoperative in the single-tie mode. This is accomplished by directing the supply air through branch 474 into passage 478 of solenoid valve 330 and on into the head end of the servo-motor 324 through line 480. The exhaust air is taken from behind the piston through line 482 and exhaust passage 484 of the valve to the atmosphere. Spring 486 normally biases valve 330 into the position above-described. Upon energization of valve solenoid 488, that is connected into the circuit through mode selector switch 490 (FIGURE 22) being turned into double-tie position, valve 330 shifts to the left connecting the plant air into line 482 by valve passage 492 thus extending piston rod 322 and exhausting the air ahead thereof through line 480 and valve passage 494 to the atmosphere. Valve 330 can be actuated as long as the mode selector switch 490 lies in the double-tie mode.

Extension and retraction of the stop 284 in the doubletie mode is brought about by simultaneous actuation of pneumatic servo-motors 308 and 324. Valve 328 which controls the servo is identical in all respects to valve 330 and includes a passage 496 that connects supply line branch 476 into line 498 entering the head end of cylinder 308 thereby retracting piston 306. Air is exhausted from behind the piston through line 500 that includes one of the previously-described feed control valves 442 and from there through passage 502 in the solenoid valve 328 to the atmosphere. Spring 504 normally biases valve 328 into the position just described. Solenoid 506 acts upon energization due to actuation of trigger 114 to connect air supply line 476 into line 500 through passage 508. Ball check 444 passes the air freely in behind the piston of servo 308 in this direction and the air is exhausted to the atmosphere through line 498 and valve passage 510. Solenoid 506 is de-energized along with the follower assembly 34 when switch 186C is actuated in single-tie mode or upon actuation of switch 186B in double-tie mode. The exhaust rate is controlled by adjustable bleed orifice 446 in valve 442 such that the piston 306 and stop mechanism attached thereto retracts rather slowly. The

rate is selected such that in double-tie mode, rollers 300 will move from position B to position C of FIGURE 17 while the first tie is being made.

The last of the elements of the pneumatic system is pneumatic servo-motor 30 that operates the ejector. Branch supply line 512 from manifold 412 is normally blocked off by control valve 514 as is branch 516 by valve 518. Valve 514 is normally biased by spring 520 into the position shown where its exhaust passage 522 is connected by line 524 into the rear end of servo 30 through feed control valve 442. In the same manner, the head or front end of servo 30 is, likewise, normally open to the atmosphere through line 526, another feed control valve 442 and exhaust passage 528 in valve 518, spring 530 biasing valve 518 into this position. Thus, the piston 532 of servo-motor 30 is free to float in the cylinder under normal conditions and compression spring 372 will, therefore, extend same slightly pushing the ejector slide 354 forward from under cover plate 378 far enough to allow flipper 380 to pop up behind a stack ready to eject it once the tie is complete.

Upon completion of one tie in single-tie mode or completion of the second tie in double-tie mode, actuation of switch 280 by cam 278 on the tyer energizes solenoid 534 of valve 514 thus connecting the branch supply line 512 into line 524 through valve passage 536 thereby extending piston 532 and ejecting the bundle. The front of the cylinder is, of course, still open to the atmosphere through valve 518.

As the ejector reaches the end of its travel it strikes a limit switch 538 (FIGURE 22) that de-energizes solenoid 534 allowing spring 520 to return valve 514 to exhaust position where the air is bled from behind piston 532 at a controlled rate through valve 442. Switch 538, upon actuation, also energizes solenoid 540 of valve 5118 con necting the supply air into the head of cylinder 30 through passage 542, valve 442 and line 526, thus retracting the ejector and exhausting air from behind the piston through valve 514 which is now open. Note, however, that with valve 518 actuated, piston 532 will be fully retracted thereby compressing spring 372 and causing the flipper 280 to fold down under cover plate 378 as shown in FIGURE 13. In this position, an incoming stack can pass right over the top of the ejector, however, as soon as the stack leaves trigger 114, the latter de-energizes solenoid 540 releasing piston 532 into float position and allowing spring 372 to extend the ejector to the point where flipper 280 will pop-up behind the stack that has just passed.

Now to FIGURE 22 for a detailed description of the electrical circuit and the operating cycle of the assembly in its various modes. The simplest of the three modes of operation is the manual-mode which will be described first. Mode selector switch 544 is set in manual mode closing contacts 544(1) while leaving contacts 544(2) and 544(3) open. Tyer feeder motor control switch 546 will be closed thereby actuating tyer feeder motor control relay 548 and closing contacts 548(1) thereof. In the manual mode, switch 550 controlling the tyer feeder hydraulic motor relay 552 is left open as the hydraulic system is inoperative.

With mode selector switch contacts 544(1) closed the tyer foot switch 272 is connected into the circuit as well as clock timer 470. When the foot switch is depressed and held down to actuate the tyer, clock timer 470 is also energized. As soon as the time interval set in the timer corresponding to the completion of the tie has elapsed, the timer opens timer limit switch 553 and shuts off the tyer.

The only other mechanism that is actuated in manual mode is solenoid 540 of the valve 518 which urges the ejector into fully-retracted position against the bias of spring 372. This solenoid remains actuated at al times when the unit is in manual mode through the normallyclosed contacts 554(1) of relay 554 and normally-closed contacts 556(1) of relay 556. Otherwise, the piston 532 of servo-motor 30 would be in float position allowing the ejector to extend slightly under the influence of spring 15 372 thus raising the flipper 280 into position to interfere with incoming stacks.

Next, the single-tie mode wherein mode-selector switch 544 is actuated to tie-energize contacts 544(1) while energizing contacts 544(2) and 544(3) will be described in detail. Tyer feed motor control relay 548 and its contacts 548(1) are energized as in the manual mode by closing switch 546. Switch 550 controlling the tyer feeder hydraulic pump relay 552 is also closed in both the single and double-tie modes to connect the hydraulic system into the feeder. Double tie relay 558, however, remains deenergized as the switch 550 controlling same is left open in single-tie mode.

Now, a bundle entering the feeder will pass onto trigger 114 closing normally-open contacts 114(1) thereof to actuate relay 560 through normally-closed contacts 562(1) of relay 562, 554(2) of relay 554 and 556(2) of relay 556. When relay 560 closes, normally-open contacts 560(1), 560(2), 560(3), and 560(4) thereof close while its normally-closed contacts 560(5) and 560(6) open. When contacts 560(1) close, normally-closed contacts 280(1) of the tyer trip switch 280 and normallyclosed contacts 186B(2) of switch 1863 complete the circuit to hold relay 560 energized. Normally-closed contacts 558(1) of the double-tie relay 558 shunt around contacts 186B(2) of switch 186B so that when the latter is opened by switch actuator 190 as the follower passes by, relay 560 will remain energized. The stack resting on 114 also opens normally-closed contacts 114(2) thereof but they close as soon as the stack passes on. Even though normally-open contacts 114(1) spring back open, as soon as the stack passes, relay 560 is held closed as previously mentioned permitting relay 562 to actuate through reclosed contacts 114(2), closed contacts 560(2) and normally-closed contacts 554(3) of relay 554.

As relay 562 actuates, its normally-open contacts 562(2), 562(3), 562(4), 562(5) and 562(6) close while normally-closed contacts 562(1) and 562(7) open. If a second stack arrives to trip trigger 114 and open contacts 114(2), relay 562 remains energized through contacts 562(3) which shunt around 114(2), 554(3) and 560(2). The stack having passed trigger 114 is in position to be pushed into the tyer by the follower assembly 34. This is accomplished through normally-closed three-way switch 564, a normally-closed wire break detector switch 566 and olosed contacts 560(3) and 562(4) which complete a circuit through solenoid 396 that extends piston rod 166 of hydraulic servo-motor 154. In the event the tyer wire has broken, detector switch 566 will open stopping the follower assembly. Switch 564 can then be opened manually to leave the follower assembly sitting still while the wire is repaired and switch 566 reclosed. Then, when everything is ready to go again, switch 564 can be reclosed to start up the follower and complete the tying cycle.

At the same time the hydraulic system is actuated to extend the follower, closing of contacts 562(6) has energized solenoid 436 to extend both the follower flap 212 andthe squaring flap 220 into position to engage the left rear corner of the stack. Closure of these same relay contacts 562(6) energizes the retractable bundle stop solenoid 506 through normally-closed contacts 568(1) of relay 568 thus bringing the retractable stop into singletie position A of FIGURE 17.

Switch actuator 190 will pass switch 186B opening contacts 186B(2) but leaving relay 560 energized through 558(1). Closing normally-open contacts 186B(1) of switch 186B has no effect yet because contacts 556(3) of relay 556 remain open. Up until relays 560 and 562 actuated to close 560(3) and 562(4) energizing solenoid 396 that moves the follower away from switch 186A, the follower held the latter open and prevented relay 556 from being actuated. As soon, however, as the follower began to move, switch 186A closed. Meanwhile, normally-closed contacts 560(5) and 562(7) had opened preventing relay 556 from being actuated until the switch operator reached switch 186C and closed same thus actuating relay 556 through normally-closed contacts 558(2) of double-tie relay 558. Back at the time the feeder was started, solenoid 540 was immediately energized to fully retract the piston of pneumatic servo-motor 30 against the bias of spring 372 just as in the manualmode already described. As before, this was necessary to hold the flipper 280 in its retracted position beneath the cover plate so as to not interfere with an incoming stack. Once the stack has passed trigger 114 and is in position to be tied, however, the flipper 280 can move up into position behind the stack ready to eject the tied bundle. Thus, when switch 186C is tripped signifying that the stack is ready to be tied, normally-closed contacts 556(1) of relay 556 that has just been actuated, open to deenergize solenoid 540 allowing the piston of pneumatic motor 30 to float so spring 372 can partially extend the ejector and raise the flipper 280.

Actuating relay 556 also de-energizes relay 562 when normally-closed contacts 556(4) open. Relay 560, on the other hand, remains actuated through normally-closed double-tie relay contacts 558(1) and, in addition, because normally-open contacts 556(5) close shunting switch contacts 186B(2). With relay 562 dc-energized, contacts 562(4) open to de-energize solenoid 396 that controls extension of the follower assembly. At the same time, normally-open contacts 556(7) close actuating solenoid 402 that reverses the follower assembly and starts same retracting. As the follower starts to retract it allows switch 186C to reopen, however, normally-open contacts 556(6) have, in the meantime, closed to keep relay 556 energized. During the retraction stroke of the follower assembly it, once again, closes normally-open contacts 186B(1) of switch 186B, but, this time normally-open contacts 556(3) are closed completing the circuit to relay 554. Normallyclosed contacts 554(1), 554(2) and 554(3) open at this point but have no effect as the relays in the circuits containing same are already de-energized (540) or by-passed by shunt circuits to remain energized.

Closing relay 556 has caused its normally-open contacts 556(8) to close completing the circuit to clock timer 470 through normally-open contacts 560(4) of relay 560 which is still closed. This starts the time cycle for the tyer and, in a branch of the same circuit, has energized the tyer foot pedal solenoid 462 through normally-closed timer limit switch 553. Upon completion of the preset interval of the clock-timer 470, it automatically de-energizes opening timer limit switch 553 and releasing the tyer foot pedal 272 when the tyer foot pedal solenoid 462 is de-energized.

Relay 556 is only going to remain actuated during the interval it takes for the follower assembly to move back from switch 186C to switch 186A because, when the latter switch is opened by return of the follower assembly, relay 556 is de-energized. As it de-energizes, normally-open contacts 556(7) again open stopping the follower because the solenoid 402 controlling the return stroke thereof is no longer energized. When relay 556 drops out of the circuit, normally-open contacts 556(8) would de-energize the clock timer 470 except that relay 554 has actuated in the interim and normally-open contacts 554(5) thereof shunt across contacts 556(8) to keep the clock timer actuated.

Another operation was accomplished when relay 556 dropped out of the circuit and deactivated relay 562. This reopened contacts 562(6) de-energizing solenoid 436 which had extended both the follower flap and squaring flap. Spring 418 could then return valve 416 to its original position where the supply air extends piston rod 230 to retract follower flap 212 and, simultaneously, retract piston rod 242 to retract the squaring flap 220.

At this point, the tyer is tying the bundle, the follower is retracting with the follower flap and squaring flaps folded, and the ejector is slightly forward with its flipper raised behind the bundle. Then, at or just after the clock timer 47.0 and timer limit switch 553 cooperate to release the tyer foot pedal 272, cam-actuated switch 280 will trip opening normally-closed contacts 280(1) to drop relay 560 out of the circuit. As cam-actuated switch 280 trips, its normally-open contacts 280(2) will close but fail to re-energize relay 568 even though contacts 556(4) are again closed because relay 562 is still out and the circuit is broken through normally-open contacts 562(2). In fact, relay 568 does not actuate at all in the single-tie mode, its function being to hold relay 560 locked in when in double-tie mode when switch 280(1) is tripped at the .end of the first tie.

Tripping cam-actuated limit switch 280 signals completion of the tie and the tied bundle is ready to be ejected. Relay 560 has been dropped out of the circuit by contacts 280(1) opening, therefore, its normally-closed contacts 560(6) are again closed. At this point the follower assembly is back in its original position holding switch 186A open and dropping relay 556 out of the circuit which lets its normally-closed contacts 556(4) reclose. Relay 562, while ready to actuate, has not done so and bundle eject forward solenoid 534 cannot be energized through contacts 562(5). Contacts 560(6) do not close until the tie is completed so the bundle will not be ejected prematurely.

The final step in the cycle is opening limit switch 538 upon completion of the forward stroke of the ejector. This drops out relay 554 opening contacts 554(6) to deenergize the bundle eject forward solenoid 534. At the same time, normally-closed contacts 554(1) return to their closed position upon deactivation of relay 554 completing the circuit to bundle eject reverse solenoid 540 through the previously closed contacts 556(1) of relay 556 which dropped out when switch 186A opened. Thus, the ejector will retract ready for the next cycle. At this point, all the relays are deactivated which is the same condition they were in at the beginning of the single-tie cycle.

Finally, the changes brought about in the cycle abovedescribed by switching in double-tie relay 558 will be examined. Relay 558 is energized by closing double-tie mode selector switch 490. In double-tie mode, the normally-closed contacts 558(1) and 558(2) open and remain open throughout the entire cycle; whereas, its normally-open contacts 558(3) and 558(4) close and remain closed.

As before, bundle eject reverse solenoid 540 is energized holding the ejector fully retracted. An incoming stack momentarily closes contacts 114(1) energizing relay 560 which holds through contacts 1863(2), 280(1) and 560(1). Contacts 558(1) are, however, now out of the circuit and they no longer shunt across contacts 1863(2). When the bundle releases switch 114, its contacts 114(2) again close energizing relay 562 through contacts 560(2) that just closed. Relay 562 holds through contacts 562(3).

In double-tie mode, when relay 562 is energized, its normally-open contacts 562(6) close and energize the solenoid 488 through closed double-tie relay contacts 558(4). This immediately repositions the retractable stop assembly as previously mentioned so that upon actuation of relay 506, the stop will move all the way around to position B of FIGURE 17.

Just as in the single-tie mode, the follower assembly is actuated forward by energizing solenoid 396 through switches 564 and 566 along with the contacts 560(3) and 562(4) of relay 560 and 562 which have closed. Closing contacts 562(6) that energized solenoid 488 also energized solenoid 436 which swung the follower flap and 560 drops out of the circuit because these contacts are no longer shunted by contacts 558(1). When relay 560 drops .out, so does solenoid 402 that has been extending the follower when contacts 560(3) open. This stops the stack short of its single-tie position up against the retractable stop in position B. The follower does not retract yet because relay 556 has not closed that control contacts 556(7). As soon as relay 560 drops out with relay 562 still in, the clock timer can actuate through normally-closed contacts 560(6) and normally-open contacts 562(5) thereby energizing the foot pedal solenoid 462 to start the tyer. Completion of the pre-set time interval will open switch '553 and de-energize solenoid 462 as soon as the tie is finished.

When the tie is finished, cam-actuated limit switch 280 will be tripped closing normally-open contacts 280(2) thereof which energize solenoid 568 through closed contacts 562(2) of actuated relay 562 and normally-closed contacts 556(4) of relay 556 which has yet to be actuated. Actuating relay 568 closes normally-open contacts 568(2) that shunt across contacts 280(2) and contacts 562(2) thus holding relay 568 until relay 556 is energized. Normally-open contacts 568(3) close by-passing open contacts 186B(2), 280(1) and 560(1) thereby re-energizing relay 560.

With relay 560 once again energized, the follower begins to move forward again due to reactivation of solenoid 396 occasioned by closing contacts 560(3). When the follower passes switch 186C, nothing happens because contacts 558(2) are open. On the other hand, contacts 558(3) of the double-tie relay are closed and when the switch operator 190 reaches switch 186D to close it, relay 556 will be energized because switch 186A closed as soon as the follower started to move forward. Closing relay 556 opens contacts 556(4) to drop relays 562 and 568 out of the circuit. When relay 568 goes out, contacts 568(3) open and relay 560 would drop out were it not for the fact that the normally-closed contacts 280(1) of switch 280 have returned to closed position following completion of the first tie and contacts 186B(2) are, likewise, again .closed completing the circuit through holding contacts 560(1). Contacts 556(5) are also closed shunting contacts 186B(2) so that relay 560 will not open when the switch operator 190 passes switch 1863 during the return stroke of the follower assembly.

When relay 562 dropped out, contacts 562(4) opened to deenergize relay 396 and stop further forward movement of the follower assembly. At the same time, relay 556 actuating closed contacts 556(7) and energized solenoid 402 to start the follower assembly on its retraction stroke. Dropping out relay 562 opened contacts 562(6) and de-energized solenoids 506, 436 and 488, to retract the follower and squaring flaps and deactivate both cylinders of the retractable stop assembly so that it starts to return slowly to its original position. Solenoid 540 has also become de-energized when relay 556 actuated to open contacts 556(1). Therefore, the ejector piston moved forward to float position with the flipper up behind the bundle.

As the follower retracts past switch 186B, it opens shunted contacts 186B(2) but leaves relay 560 closed. At the same time, it closes contacts 186B(1) momentarily and energizes relay 554 through closed contacts 556(3). Relay 554 then holds through ejector limit switch 538 and holding contacts 554(4).

Still another function is performed by closing relay 556 because its contacts 556(8) coupled with closed contacts 560(4) of actuated relay 560 start the clock timer actuating the tyer foot pedal solenoid 462 to start the second tie. Note that by energizing the clock timer through contacts 556(2) of relay 556, the second tie begins just as soon as the follower assembly has reached switch 186D and pushed the stack up against the retreating stop assembly that has retracted to approximately position C in FIGURE 17. Otherwise, energization of the sec- 19 nd tie cycle would have been delayed until the follower assembly retracted to switch 186B and relay 554 had actuated to close contacts 554().

The sole remaining function to be performed is to eject the double-tied bundle. Once again, cam-actuated switch 280 will be tripped upon completion of the second tie dropping out relay 560. Contacts 280(2) of this switch will close momentarily but be ineffectual to reactuate relay 568 because contacts 562(3) are open, relay 562 having been dropped out by relay 556 opening contacts 556(4). These contacts 556(4) will not close again until the fol lower assembly fully retracts and trips switch 186A deactivating relay 556, but, in the mean-time, relay 554 has actuated opening contacts 554(3) which keep relay 562 from again actuating.

At the time relay 554 actuates, relay 560 has dropped and so that the bundle eject forward solenoid 534 can be actuated through normally-closed contacts 560(6) and the closed contacts 554(6) of relay 554. When the ejector reaches limit switch 538 and trips same, contacts 554(4) will open dropping out relay 554 to deenergize the bundle eject forward solenoid 534. The follower assembly has already returned to starting position, opened switch 186A and de-energized relay 556 so that contacts 556(1) are, once again closed. Thus, when relay 554 drops out, its normally-closed contacts 554(1) can again close energizing bundle eject reverse solenoid 540 that returns the ejector to its fully-retracted position. As before, all the relays with the exception of double-tie relay 558 are deenergized preparatory to receiving another stack and only solenoid 540 is actuated.

Having thus described the several useful and novelfeatures of the tyer feeder of the present invention, it will be seen that the several worthwhile objects for which it was designed have been achieved. Although but a single specific embodiment of the invention has been illustrated and specifically explained, we realize that certain modifications may well occur to those skilled in the art Within the broad teaching hereof; hence, it is our intention that the scope of protection afforded hereby shall be limited only insofar as said limitations are expressly set forth in the appended claims which follow.

What is claimed is:

1. A device for feeding stacks of loosely-layered articles to a bundling machine, positioning the stack for application of a tie thereto and ejecting the tied bundle which comprises: conveyor means adapted to accept a stack of loosely-layered articles and deliver same over the discharge end thereof to a bundling machine aligned therewith; retractable stop means spaced beyond the discharge end of the conveyor means operable upon actuation to move into the path of an incoming stack and stop sarne into position to be tied; stack-feeding means mounted to one side of the conveyor means adapted upon actuation to engage a stack on the conveyor means and push same off the discharge end thereof and up against the retractable stop means when the latter is in extended position, said feeding means including a feeder ram mounted for reciprocating motion and a pusher flap carried by said ram for movement therewith between a retracted position bypassing an incoming stack into an extended position behind the latter; and bundle ejecting means located adjacent the discharge end of the conveyor means operative upon actuation to engage the rear face of the bundle and stack-feeding means includes a feeder ram servo-motor operatively connected to the feeder ram and adapted upon actuation to bring aboutreciprocating movement thereof,

a feeder-servo directional control valve connected to the feeder ram servo-motor, said directional control valve having a feed position adapted to actuate the feeder ram servo-motor in a direction to extend the feeder ram: a return position adapted to actuate the feeder ram servo motor in a direction to retract the feeder ram, and a float position by-passing said feeder ram servo-motor so as to stop said feeder rarn in any position throughout its cycle of reciprocal movement.

3. The device as set forth in claim 1 in which: the stackfeeding means includes a pusher-flap servo-motor operatively connected to the pusher flap and adapted upon actuation to shift same between its retracted and extended positions; and, a flap directional control valve having a feed position operative to actuate the pusher-flap servomotor in a direction to extend the pusher-flap and also a return position operative to actuate said flap-servo in direction to retract said flap.

4. The device as set forth in claim 1 in which: the retractable stop means includes a pivotal element mounted for arcuate movement from a retracted position alongside a bundle being ejected to an extended position blocking an incoming stack; a primary retractable stop servo-motor connected to the pivotal element and operative upon actuation to swing same between its extended and retracted position, and a primary stop servo directional control valve connected to the primary servo, said primary servo valve having a feed position operative to actuate the primary servo in a direction to extend the pivotal element and also a return position operative to actuate said primary servo in a direction to retract said pivotal element.

5. The device as set forth in claim 1 in which: the bundle ejecting means includes an ejector ram servo-motor connected to the ejector ram and operative upon actuation to bring about reciprocating movement thereof, first spring means connected to the ejector ram servo and operative to normally bias same in a direction to partially extend the ejector ram, second spring means interconnecting the ejector ram and flipper operative to normally bias the latter into an upright operative position, stationary means overlying the ejector ram in the path of the flipper, said stationary means being adapted to engage said flipper and fold same down out of the way of an incoming stack upon retraction of the ejector ram beyond the partially-extended position in which said ram is placed by the first spring means, an ejector ram retraction control valve connected to the ejector ram servo-motor operative upon actuation to fully retract the ejector ram against the bias of the first spring means and fold down the flipper under the stationary means, and an ejector ram extension control valve connected to the ejector ram servo operative upon actuation to energize same in a direction to extend the ejector ram.

6. The device as set forth in claim 1 which includes: stack-sensing means located in the path of an incoming stack and operatively connected to the stack-feeding means and retractable stop means, said stack-sensing means being responsive to movement of a stack across the roller conveyor means and adapted upon actuation thereby to extend 'both the stack-feeding means and retractable stop means so as to locate the stack in the bundling machine in position to have a tie applied thereto.

7. The device as set forth in claim 2 which includes: stack-sensing means positioned in the path of an incoming stack and connected to the feeder ram servo directional control valve, said stack sensing means being responsive to the presence of an incoming stack so as to actuate said feeder ram servo directional control valve into its feed position; single-tie limit means positioned in the path of the feeder ram and connected to its directional control valve, said single-tie limit means being responsive to the arrival of said ram at a position where the feeder means has pushed a stack into position to have a tie affixed approximately midway between the ends thereof so as to actuate said directional control valve into its return position; and feeder ram retraction limit means positioned in the path of the feeder ram and connected to its directional control valve, said ram retraction limit means being responsive to return of the feeder ram into fully retracted position so as to actuate said directional control valve into its by-pa-ss position.

8. The device as set forth in claim 2 which includes: stack-sensing means positioned in the path of an incoming stack and connected to the feeder ram servo directional control valve, said stack-sensing means being responsive to the presence of an incoming stack so as to actuate said feeder ram servo directional control valve into its feed position; first double-tie limit means positioned in the path of the feeder ram and connected to its directional control valve, said first double-tie limit means being responsive to arrival of said ram at a position where the feeder means has pushed a stack into position to have a tie afiixed adjacent the lead end thereof so as to actuate said directional control valve into its by-pass position; tie-completion sensing means connectable to the bundling machine and operative when so connected to signal completion of a tie, said tie-completion sensing means 'being also connected to the feeder ram servo directional control valve and adapted to shift same into feed position following energization of the first doubletie limit means and completion of a tie adjacent the lead end of a stack; and second double-tie limit means positioned in the path of the feeder ram and connected to its directional control valve, said second double-tie limit means being responsive to the arrival of said ram at a position where the feeder means has pushed a stack into position to have a second tie affixed adjacent the following end thereof so as to actuate said directional control valve into its return position.

9. The device as set forth in claim 3 in which: the stack-feeding means includes a squaring flap carried by the feeder ram for movement from a retracted position bypassing an incoming stack to an extended position engagement with the adjacent side thereof, and a squaringfiap servo-motor connected to the squaring flap and operative upon actuation to move same between its extended and retracted positions, said squaring flap servomotor being also connected tothe flap directional control valve, said flap directional control valve being-operative in feed position to actuate the squaring flap servomotor in a direction to extend the squaring flap and operative in return position to actuate said servo-motor in the direction to retract same.

10. The device as set forth in claim 4 in which: the retractable stop means includes a secondary retractable stop servo-motor operatively linked to the primary retractable stop servo-motor and adapted upon actuation to shift the latter along with the pivotal element connected thereto in the direction of extended movement, said primary retractable stop servo-rnotor being adapted upon actuation to swing the pivotal element into position to stop an incoming stack at a point relative to the bundling machine where the latter will apply a tie approximately midway between the ends of said stack, said primary and secondary retractable stop servo-motors cooperating when both are actuated to swing said pivotal element into position to stop an incoming stack at a point relative to the bundling machine where the latter will apply a tie adjacent the lead end thereof, a secondary retractable stop servo-motor directional control valve connected to the second retractable stop servo-motor, said secondary directional control valve having a feed position operative to enerize its servo-motor in the direction to shift the primary retractable stop servo-motor and pivotal element connected thereto toward extended position, and said directional control valve having a return position operative to energize its servo-motor in the direction to retract the primary servo-motor and pivotal element.

11. The device as set forth in claim 5 which includes: tie-completion sensing means connected to the ejector 22 ram extension control valve adapted upon actuation to energize same into position to extend the ejector ram, said tie-completion sensing means being connectable to the bundling machine and operative when so connected to actuate the ejector ram extension control valve following application of a tie to a stack; ejector ram extension limiting means positioned in the path of the ejector ram and connected to the ejector ram retractioncontrol valve, said ejector ram limiting means being responsive to extension of the ejector ram and operative when actuated thereby to energize the ejector ram retraction control valve so as to fully retract the ejector ram; and stack-sensing means positioned in the path of an incoming stack and connected to the ejector ram retraction control valve, said stack-sensing means being operative upon actuation by an incoming stack to de-energize the ejector ram retraction control valve allowing the first spring means to partially extend the ejector ram from underneath the stationary means so that the second spring means can lift the flipper up behind said stack.

12. The device as set forth in claim 7 which includes: tyer interlock means connectable to the bundling machine and operative when so connected to actuate same, said interlock means also being connected to the single-tie limit means and responsive to actuation thereof to start the bundling machine.

13. The device as set forth in claim 8 which includes: tyer interlock means connectable to the bundling machine and operative when so connected to actuate same, said tyer interlock means also being connected to both the first and second double-tie limit means and responsive to actuation of both said double tie limit means to actuate the bundling machine.

14. The device as set forth in claim 8 in which: the retractable stop means includes a pivotal element mounted for arcuate movement between a retracted position to one side of a bundle being ejected and an extended position blocking the path of an incoming bundle, a primary retractable stop servo-motor connected to the pivotal element and adapted upon actuation to swing same between its extended and retracted positions, a primary retractable stop servo-motor directional control valve connected to said primary retractable stop servo-motor, said primary motor control valve having a feed position operative to actuate said servo-motor connected thereto so as to extend the pivotal element to a position adapted to stop an incoming stack in the bundling machine at a point where the latter will apply a tie approximately midway between the ends thereof, and said primary motor control valve having a return position operative to energize said primary in a direction to retract the pivotal element, a secondary retractable stop servo-motor operatively linked to the primary retractable stop servo-motor and adapted upon actuation to shift both said primary servo-motor and the pivotal element attached thereto in the direction of extended movement, a secondary retractable stop servo-motor control valve connected to said secondary retractable stop servo-motor, said secondary motor control valve having a feed position operative to shift both said primary servo-motor and pivotal link toward an extended position, and said secondary motor control valve having a return position operative to shift 56th said primary servo-motor and pivotal element into a retracted position, said primary and secondary retractable stop servo-motors cooperating with one another when both are actuated into their extended positions to swing the pivotal element to an over-extended position relative to the bundling machine where an incoming stack will be stopped at a point where the tie will be affixed adjacent the lead end thereof, and bleed control means connected to the primary and secondary retractable stop servo-motor control valves, said bleed control means being operative when said valves are shifted into return position to control the rate of pivotal element retraction such that said 

1. A DEVICE FOR FEDDING STACKS OF LOOSELY-LAYERED ARTICLES TO A BUNDLING MACHINE, POSITIONING THE STACK FOR APPLICATION OF A TIE THERETO AND EJECTING THE TIED BUNDLE WHICH COMPRISES: CONVEYOR MEANS ADAPTED TO ACCEPT A STACK OF LOOSELY-LAYERED ARTICLES AND DELIVER SAME OVER THE DISCHARGE END THEREOF TO A BUNDLING MACHINE ALIGNED THEREWITH; RETRACTABLE STOP MEANS OPERABLE UPON ACTUATION TO END OF THE CONVEYOR MEANS OPERABLE UPON ACTUATION TO MOVE INTO THE PATH OF AN INCOMING STACK AND STOP SAME INTO POSITION TO BE TIED; STACK-FEEDING MEANS MOUNTED TO ONE SIDE OF THE CONVEYOR MEANS ADAPTED UPON ACTUATION TO ENGAGE A STACK ON THE CONVEYOR MEANS AND PUSH SAME OFF THE DISCHARGE END THEREOF AND UP AGAINST THE RETRACTABLE STOP MEANS WHEN THE LATTER IS IN EXTENDED POSITION, AND FEEDING MEANS INCLUDING A FEEDER RAM MOUNTED FOR RECIPROCATING MOTION AND A PUSHER FLAP CARRIED BY SAID RAM FOR MOVEMENT THEREWITH BETWEEN A RETRACTED POSITION BYPASSING THE INCOMING STACK INTO AND AN EXTENDED POSITION BEHIND THE LATTER; AND BUNDLE EJECTING MEANS LOCATED ADJACENT THE DISCHARGE END OF THE CONVEYOR MEANS OPERATIVE UPON ACTUATION TO ENGAGE THE REAR FACE OF THE BUNDLE AND PUSH SAME FROM THE BUNDLING MACHINE UPON COMPLETION OF THE TIE AND FOLLOWING RETRACTION OF THE RETRACTABLE STOP MEANS, SAID EJECTING MEANS INCLUDING AN EJECTOR RAM MOUNTED FOR RECIPROCATING MOTION AND A FLIPPER HINGEDLY ATTACHED TO THE END OF THE EJECTOR RAM OPERATIVE UPON EXTENSION OF THE LATTER FLIP UP AUTOMATICALLY INTO POSITION BEHIND THE TIED BUNDLE. 